CN110671196A - Engine - Google Patents
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- CN110671196A CN110671196A CN201811639121.5A CN201811639121A CN110671196A CN 110671196 A CN110671196 A CN 110671196A CN 201811639121 A CN201811639121 A CN 201811639121A CN 110671196 A CN110671196 A CN 110671196A
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- piston
- connecting rod
- engine
- compression ratio
- control rod
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/047—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of variable crankshaft position
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
The invention discloses an engine. The engine includes: a piston movable within a cylinder of the engine; bent axle, cover establish adjusting element on the connecting rod neck, the connecting rod of connecting piston and adjusting element, compress and press ratio adjustment mechanism and adjust the piston position, it includes: the distance between the central axis of the driving shaft and the central axis of the main journal is L5, the distance between the center of the eccentric wheel and the central axis of the driving shaft is R2, the distance between the first end hinge center of the control rod and the center of the eccentric wheel is L4, and L5, R2 and L4 satisfy the following relations: L5-R2 < L4 < L5+ R2. According to the engine, the arrangement position and the size of parts in the compression ratio adjusting mechanism are changed, so that the motion trail of the first end of the control rod is close to the rotation center of the crankshaft, the vibration generated in the swinging process of the control rod is reduced, and the vibration and the noise of the whole engine are reduced.
Description
Technical Field
The invention relates to the field of automobiles, in particular to an engine.
Background
The compression ratio of the engine is the ratio of the volume of the cylinder when the piston moves to the bottom dead center to the volume of the combustion chamber when the piston moves to the top dead center. Most of the existing engines are fixed compression ratio engines, and have low fuel combustion efficiency, poor economical efficiency and high emission. With the development of variable compression ratio technology, engines have begun to incorporate compression ratio adjustment mechanisms to vary the compression ratio by varying the combustion chamber volume by, for example, varying the piston top dead center position.
The theory of thermal efficiency shows that the higher the compression ratio is, the higher the thermal efficiency is, and the lower the oil consumption is, however, the knock can be caused by increasing the compression ratio, and in consideration of suppressing the knock, the upper limit of the compression ratio is limited, most of the existing engines are fixed compression ratio engines, and the balance between high thermal efficiency and suppressing the knock can not be realized; in addition, in various conventional compression ratio adjusting mechanisms, the problems of more parts, large mechanism vibration, large noise and the like generally exist.
Disclosure of Invention
In view of the above, the present invention is directed to an engine to improve NVH performance of the engine.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
an engine comprising: a piston movable within a cylinder of the engine; the main journal of the crankshaft is rotatably arranged on a cylinder body of the engine, and the connecting rod journal of the crankshaft is staggered with the central axis of the main journal; the adjusting element is sleeved on the connecting rod neck; a connecting rod connected between the piston and the adjustment element; a compression ratio adjustment mechanism for adjusting a position of the piston within the cylinder, the compression ratio adjustment mechanism comprising: the eccentric shaft and the control rod are connected between the adjusting element and the eccentric shaft, and the control rod is eccentrically connected with the eccentric shaft, so that when the eccentric shaft rotates, the adjusting element can rotate around a connecting rod neck sleeved with the adjusting element.
The eccentric shaft includes: the driving shaft is rotatably arranged on the cylinder body, the eccentric wheel is sleeved on the driving shaft, the first end of the control rod is hinged to the adjusting element, and the second end of the control rod is hinged to the driving shaft through the eccentric wheel. A distance between a central axis of the driving shaft and a central axis of the main journal is L5, a distance between a center of the eccentric and the central axis of the driving shaft is R2, a distance from a first end hinge center of the control lever to the center of the eccentric is L4, and L5, R2, and L4 satisfy the following relations: L5-R2 < L4 < L5+ R2.
According to some embodiments of the invention, the distance between the center of the eccentric and the central axis of the main journal is L46, the difference between the distances L46 and L4 is L, L satisfying the relation: l is less than 5 mm.
According to some embodiments of the invention, the distance between the center of the eccentric and the central axis of the main journal is L46, the difference between the distances L46 and L4 is L, L satisfying the relation: l is less than 1 mm. The smaller L, the smaller the fourth order vibrations generated by the control lever during oscillation. Further, when L is 0, the fourth order vibration generated by the lever during the swing disappears.
According to some embodiments of the invention, the engine has a minimum compression ratio when the compression ratio adjustment mechanism is adjusting the piston to a first extreme position; when the compression ratio adjustment mechanism adjusts the piston to a second limit position, the engine has a maximum compression ratio.
During the movement of the piston from the first extreme position to the second extreme position, L-0 is present.
Optionally, when the piston is in the first extreme position, L is 0.
According to some embodiments of the invention, the length of L46 when the piston is in the first extreme position is smaller than the length of L46 when the piston is in the second extreme position.
Further, the compression ratio adjustment mechanism further includes: and the driving device is connected with the driving shaft and is used for driving the driving shaft to rotate.
According to some embodiments of the invention, the first end of the connecting rod is hinged to the piston by a piston pin and the second end of the connecting rod is hinged to the adjusting element by a connecting rod pin.
Further, the first end of the control rod is hinged to the adjusting element through a control rod pin, and the connecting rod pin and the control rod pin are arranged on two sides of the connecting rod neck.
Compared with the prior art, the engine has the following advantages:
the engine has the advantages that the number of parts of the compression ratio adjusting mechanism is small, so that the purpose of changing the compression ratio can be achieved, the assembly process of the engine is favorably reduced, the number of parts is small, and the working reliability of the compression ratio adjusting mechanism is favorably improved. Through changing the arrangement position of the driving shaft on the cylinder body, the size of L5 can be changed, the sizes of R2 and L4 can be changed by reasonably designing the eccentric amount of the eccentric wheel and the length of the control rod, so that the motion track of the first end of the control rod is close to the rotation center of the crankshaft, the vibration generated by the control rod in the swinging process is reduced, the vibration and the noise of the whole engine are reduced, and the NVH performance of the whole engine is optimized.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is an assembled schematic view of a piston, connecting rod, adjustment element, crankshaft, compression ratio adjustment mechanism;
FIG. 2 is a mechanical schematic of a piston, connecting rod, adjustment element, crankshaft, compression ratio adjustment mechanism;
FIG. 3 is a dimensional schematic of a piston, connecting rod, adjustment element, crankshaft, compression ratio adjustment mechanism;
FIG. 4 is a schematic view of a piston force;
FIG. 5 is a force diagram of the piston, connecting rod, adjustment element, crankshaft, compression ratio adjustment mechanism.
Description of reference numerals:
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
The engine of the present invention will be described in detail with reference to fig. 1 to 5 in conjunction with the embodiment.
Referring to fig. 1, an engine according to an embodiment of the present invention includes: piston 1, connecting rod 2, adjusting element 3, crankshaft 4 and compression ratio adjusting mechanism 7.
The piston 1 is movable in a cylinder 8 of the engine, and as shown in fig. 1 and 4, the piston 1 is movable in the up-down direction of fig. 1 in the cylinder hole of the cylinder 8.
The main journal 41 of the crankshaft 4 is rotatably provided in the cylinder block of the engine, and the connecting journal 42 of the crankshaft 4 is offset from the central axis of the main journal 41. There may be a plurality of connecting journals 42 of the crankshaft 4.
The adjusting element 3 is sleeved on one of the connecting rod necks 42, specifically, a crank hole is formed in the adjusting element 3, the connecting rod neck 42 is located in the crank hole, and the adjusting element 3 and the connecting rod neck 42 can rotate mutually. In some embodiments, a journal pin C or bushing may be disposed between the adjustment element 3 and the journal 42 to reduce wear of the adjustment element 3 and the journal 42 and extend the service life of the engine components.
The connecting rod 2 is connected between the piston 1 and the adjusting element 3, i.e. a first end of the connecting rod 2 is connected to the piston 1 and a second end of the connecting rod 2 is connected to the adjusting element 3. Particularly, the first end of connecting rod 2 is articulated with piston 1, and the second end of connecting rod 2 is articulated with adjusting element 3, makes from this and can take place mutual rotation between connecting rod 2 and the piston 1, can take place mutual rotation between connecting rod 2 and the adjusting element 3, like this, when adjusting element 3 rotates around its connecting rod neck 42 of establishing that overlaps, can drive connecting rod 2 motion, and then drive piston 1 up-and-down motion.
The compression ratio adjusting mechanism 7 is used for adjusting the position of the piston 1 in the cylinder 8, so that the position of the piston 1 relative to the cylinder 8 is changed at the top dead center or the bottom dead center, and then the compression ratio is changed. As shown in fig. 1, the compression ratio adjustment mechanism 7 may include: the eccentric shaft 6 and the control rod 5, the control rod 5 is connected between the adjusting element 3 and the eccentric shaft 6, the first end of the control rod 5 is connected with the adjusting element 3, and the second end of the control rod 5 is eccentrically connected with the eccentric shaft 6, so that when the eccentric shaft 6 rotates, the power of the eccentric shaft 6 can be transmitted to the adjusting element 3 through the control rod 5, and the adjusting element 3 rotates around the connecting rod neck 42 sleeved with the adjusting element.
Specifically, when the eccentric shaft 6 rotates, the control rod 5 is pushed to rotate, the control rod 5 pushes the adjusting element 3 to rotate, the adjusting element 3 pushes the connecting rod 2 to rotate, and the connecting rod 2 pushes the piston 1 to move up and down, so that the position of the piston 1 in the cylinder 8 can be adjusted. The piston 1 moves up and down, changing the volume of the combustion chamber and thus the compression ratio. That is, the compression ratio adjustment mechanism 7 may function to change the engine compression ratio. By changing the compression ratio, the load requirements of different engines can be met, and the engines can always work in the optimal working area, so that the dynamic property is improved, the oil consumption is reduced, the emission is reduced, the contradiction between the dynamic property and the economical efficiency and the emission is well solved, and the engines can always work in the optimal oil consumption area.
It should be noted that, in the description of the present invention, the "first end" of the component refers to the upper end in fig. 1, and the "second end" refers to the lower end in fig. 1, but words indicating orientation such as "first end", "second end", "upper", "lower", etc. are for convenience of description only and should not be construed as limiting the present invention.
Referring to fig. 1, the eccentric shaft 6 may include: the driving shaft 61 is rotatably arranged on the cylinder body, the eccentric wheel 62 is sleeved on the driving shaft 61, and the eccentric wheel 62 is fixed relative to the driving shaft 61. A first end of the control rod 5 is articulated with the adjusting element 3 and a second end of the control rod 5 is articulated with the drive shaft 61 via an eccentric 62, whereby the control rod 5 and the adjusting element 3 and the control rod 5 and the drive shaft 61 are rotatable relative to each other.
Referring to fig. 3, the distance between the central axis 61a of the driving shaft 61 and the central axis 4a of the main journal 41 is L5, the distance between the center 62a of the eccentric 62 and the central axis 61a of the driving shaft 61 is R2, that is, the eccentric amount of the eccentric 62 is R2, the distance from the first end hinge center of the control rod 5 to the center 62a of the eccentric 62 is L4, and L5, R2, and L4 satisfy the following relations: L5-R2 < L4 < L5+ R2.
During the oscillation, the control rod 5 transmits an additional fourth order oscillation to the crankshaft 4. As shown in fig. 3, the first end of the control rod 5 has a trajectory Dc, and the distance Dc from the central axis 4a of the main journal 41 is L. When L5-R2 < L4 < L5+ R2, it is ensured that the movement locus of the first end of the control lever 5 approaches the central axis 4a of the main journal 41, i.e., that L is small, thereby facilitating reduction of the fourth order vibration generated by the control lever 5 during the swing.
In the engine of the embodiment of the invention, the compression ratio adjusting mechanism 7 has fewer parts, so that the purpose of changing the compression ratio of the engine can be achieved, the assembly process of the engine is favorably reduced, the number of the parts is fewer, and the working reliability of the compression ratio adjusting mechanism 7 is favorably improved.
Further, the compression ratio adjustment mechanism 7 may further include: and the driving device is connected with the driving shaft 61 and is used for driving the driving shaft 61 to rotate. Specifically, the drive device provides a drive torque to the drive shaft 61 to rotate the drive shaft 61.
The distance between the center 62a of the eccentric wheel 62 and the central axis 4a of the main journal 41 is L46, the absolute value of the difference between the distances of L46 and L4 is L, and when L5-R2 < L4 < L5+ R2, L satisfies the relation: l is less than 5 mm.
Preferably, when L5-R2 < L4 < L5+ R2, L satisfies the relationship: l is less than 1 mm.
During the rotation of the drive shaft 61, the distance between the center 62a of the eccentric 62 and the central axis 4a of the main journal 41 changes, i.e., the length of L changes.
When L is not equal to 0, that is, the swing locus Dc of the first end of the control rod 5 does not coincide with the central axis 4a of the main journal 41, the inertia force generated by the control rod 5 during the swing process generates an inertia torque in the rotation direction of the crankshaft 4, and the inertia torque generates an additional fourth-order vibration of the crankshaft 4, and the fourth-order vibration is superimposed with the fourth-order vibration generated during the operation of the crankshaft 4 itself, so that the crankshaft 4 vibrates greatly, and the operation stability is deteriorated. The smaller L, the smaller the fourth order vibration generated by the control rod 5 during the swing, the smaller the influence on the vibration of the crankshaft 4, and therefore, in order to reduce the vibration of the crankshaft 4, the absolute value of L should be less than 5, and preferably, the absolute value of L is less than 1.
Further, when L is 0, the first end of the control rod 5 has a motion locus Dc passing through the central axis 4a of the main journal 41, and the fourth order vibration generated during the swing of the control rod 5 disappears.
Specifically, by changing the position of the eccentric shaft 6 on the cylinder block, the size of L5 can be changed, and by reasonably designing the eccentric amount of the eccentric wheel 62 and the length of the control rod 5, the sizes of R2 and L4 can be changed, so that L5, R2 and L4 satisfy the relation: L5-R2 < L4 < L5+ R2, thereby ensuring that L is less than 5mm, even ensuring that L is less than 1 mm. That is, by optimizing the arrangement position of the eccentric shaft 6 in the compression ratio adjusting mechanism 7 and the sizes of other parts, the distance L from the rotation center 4a of the crankshaft 4 to the motion locus Dc of the first end of the control rod 5 can be made smaller, i.e., L is less than 5mm, even L is less than 1mm, so that the four-order vibration generated by the control rod 5 in the swinging process is reduced, the vibration and noise of the whole engine are reduced, and the NVH performance of the whole engine is optimized.
In the low compression ratio region, the compression ratio adjusting mechanism 7 is stressed more, moves faster and vibrates more compared with the high compression ratio region. The value in the low compression ratio region L should be smaller than that in the large compression ratio region L. In the whole compression ratio variation range, L has a position of 0, and the compression ratio corresponding to the position is the same as the compression ratio corresponding to the maximum stress of the compression ratio adjusting mechanism 7.
Specifically, when the compression ratio adjustment mechanism 7 adjusts the piston 1 to the first limit position, the engine has the minimum compression ratio; when the compression ratio adjustment mechanism 7 adjusts the piston 1 to the second limit position, the engine has the maximum compression ratio.
During the movement of the piston 1 from the first extreme position to the second extreme position, L is 0. That is, when the drive shaft 61 adjusts the piston 1 to a certain compression ratio, L46 is L4.
In some alternative embodiments, when the piston 1 is in the first extreme position, L is 0. That is, in this embodiment, when the drive shaft 61 adjusts the piston 1 to the minimum compression ratio, there is L46 — L4.
The length of L46 when the piston 1 is in the first extreme position is smaller than the length of L46 when the piston 1 is in the second extreme position. In other words, the length of L46 when the drive shaft 61 adjusts the piston 1 to the minimum compression ratio is smaller than the length of L46 when the drive shaft 61 adjusts the piston 1 to the maximum compression ratio.
A first end of the connecting rod 2 is articulated with the piston 1 by means of a piston pin a, and a second end of the connecting rod 2 is articulated with the adjusting element 3 by means of a connecting rod pin B.
Further, the first end of the control rod 5 is hinged to the adjusting element 3 through a control rod pin D, and the link pin B and the control rod pin D are disposed at two sides of the link neck 42 on which the adjusting element 3 is sleeved. In other words, the adjusting element 3 is provided with a connecting rod pin hole and a control rod pin hole which are provided on both sides of the crank hole of the adjusting element 3, and preferably, a center connecting line of the connecting rod pin hole and the control rod pin hole passes through the center of the crank hole.
The crankshaft 4 is disposed between the piston 1 and the eccentric shaft 6, thereby bringing the crankshaft 4 closer to the piston 1 so that kinetic energy of the piston 1 can be rapidly transferred to the crankshaft 4 upon combustion of fuel, reducing loss of kinetic energy.
Referring to fig. 1-2 and 4, a distance between a central axis 4a of the main journal 41 and a motion trajectory of the piston 1 is e, a distance between the connecting journal 42 sleeved by the adjusting element 3 and the central axis of the main journal 41 is R1, an included angle between a central connecting line of the connecting journal 42 and the main journal 41 and the motion trajectory of the piston 1 is CA, a distance between a connecting center of a first end of the connecting rod 2 and a connecting center of a second end of the connecting rod 2 is L1, and a distance between the connecting center of the second end of the connecting rod 2 and the center of the connecting journal 42 is L2.
An included angle between a connecting line between the connecting center of the first end of the connecting rod 2 and the connecting center of the second end of the connecting rod 2 and a connecting line between the connecting center of the second end of the connecting rod 2 and the connecting center of the first end of the control rod 5 is beta, and when CA is larger than or equal to-40 degrees and smaller than or equal to 120 degrees, L1, L2, R1, e, beta and CA meet the relation:
it should be noted that, referring to fig. 2, taking the center of the main journal 41 as the O point of the XOY coordinate system (not labeled in the figure), the horizontal axis is the X axis, and the vertical axis is the Y axis, when the central connecting line of the connecting rod journal 42 and the main journal 41 is located in the first quadrant and the fourth quadrant, CA > 0 °; when the central connecting line of the connecting rod neck 42 and the main journal 41 is positioned in the second quadrant and the third quadrant, CA is less than 0 degree; when the line connecting the centers of the connecting rod neck 42 and the main journal 41 coincides with the Y axis, CA is 0 °, and the first quadrant, the second quadrant, the third quadrant, and the fourth quadrant are sorted in a counterclockwise direction around the center of the main journal 41.
As shown in fig. 2 and 4, the distance between the center of the piston pin a and the center of the connecting rod pin B is L1, the distance between the center of the connecting rod pin B and the center of the connecting rod journal pin C is L2, the included angle between the connecting line between the center of the piston pin a and the center of the connecting rod pin B and the connecting line between the center of the connecting rod pin B and the center of the control rod pin D is β, that is, the included angle between the connecting rod 2 and the adjusting element 3 is β, the connecting rod journal 42 sleeved on the adjusting element 3 is connected with the main journal 41 through the crank 43, and the length of the crank 43 is R1.
As shown in FIG. 2, the distance between the connecting rod journal pin C and the lever pin D is L3, and L3 and L2 may or may not be equal.
The included angle between the connecting rod 2 and the motion track of the piston 1 is a1, that is, the included angle between the connecting line between the hinge center of the first end of the connecting rod 2 and the hinge center of the second end of the connecting rod 2 and the motion track of the piston 1 is a 1.
During engine operation, the piston 1 is subjected to a downward cylinder explosion pressure F. The piston 1 is pushed downwards by the force F, while the piston 1 transmits a part of the force F to the bore of the cylinder 8, this force Fx and F tan a 1. Fx is positively correlated with a1, with larger a1 giving larger Fx. Fx being too large can result in excessive wear of the piston 1 and bore of the cylinder 8.
When the angle CA is in the range of-40 to 120 °, the gas in the cylinder is in a compressed and burned state, the pressure of the gas is high, and the cylinder explosion pressure F to which the piston 1 is subjected is large. At this time, L1, L2, R1, e, β, CA satisfy the relation:
a1 is more than or equal to 0 degree and less than or equal to 8 degrees, namely the included angle A1 between the motion tracks of the connecting rod 2 and the piston 1 is 0-8 degrees, and the force Fx of the piston 1 to the cylinder hole of the cylinder 8 is always smaller.
By changing the part size of the compression ratio adjusting mechanism 7, the values of L1, L2 and R1 can be changed, and by changing the arrangement structure of the compression ratio adjusting mechanism 7, the values of e, beta and CA can be changed, so that L1, L2, R1, e, beta and CA satisfy the relational expression:ensure that A1 is more than or equal to 0 degree and less than or equal to 8 degrees.
According to the engine provided by the embodiment of the invention, the arrangement structure or the size of parts of the compression ratio adjusting mechanism 7 is adjusted, so that the included angle A1 between the motion tracks of the connecting rod 2 and the piston 1 is always smaller, the lateral acting force of the piston 1 on the cylinder hole of the cylinder 8 can be reduced, and the abrasion between the piston 1 and the cylinder hole is improved.
When CA is more than or equal to 30 degrees and less than or equal to 40 degrees, L2, R1, e, beta and CA satisfy the relation: l is2*sin(β)-R1Sin (ca) + e ≈ 0. At this time, the included angle a1 between the motion tracks of the connecting rod 2 and the piston 1 satisfies: 0 DEG-A1-0.5 DEG, and Fx F-TanA 1-0.
In other words, when the angle CA is in the range of 30 ° to 40 °, the cylinder interior gas is in the highest pressure state, and the force F received by the piston 1 is in the vicinity of the maximum value, and at this time, L2, R1, e, β, and CA should additionally satisfy the relationship L2*sin(β)-R1Sin (ca) + e ≈ 0. The included angle A1 between the motion tracks of the connecting rod 2 and the piston 1 is between 0 and 0.5 degrees, and the force Fx of the piston 1 to the cylinder hole is approximately equal to 0.
The two points can enable the force Fx of the piston 1 to the cylinder hole of the cylinder 8 to be smaller than the limit which can be born by the piston 1 and the cylinder hole in a common engine, and reduce the lateral force of the piston 1 to the cylinder hole, thereby improving the abrasion condition between the piston 1 and the cylinder hole.
Referring to fig. 1-2 and 5, during the operation of the engine, the piston 1 is subjected to a downward cylinder explosion pressure F, and the piston 1 is pushed to move downward by the force F. During the downward movement of the piston 1, the force is transmitted to the adjusting element 3 via the connecting rod 2. The adjusting element 3 receives a force Fa from the connecting rod 2, the adjusting element 3 distributes the force Fa to the crankshaft 4 and the control rod 5, the adjusting element 3 applies a force Fb to the crankshaft 4, which pushes the crankshaft 4 into a rotary motion and is converted by the crankshaft 4 into an outward power output, the adjusting element 3 applies a force Fc to the control rod 5, which force Fc is transmitted by the control rod 5 to the eccentric shaft 6 and counteracts the rotation of the eccentric shaft 6.
During the operation of the engine, it is desirable that the driving force Fb obtained by the crankshaft 4 is sufficiently large, and the engine needs to be large enough to output sufficient power. And it is desirable that the resistance Fc obtained by the eccentric shaft 6 is sufficiently small, which, if too large, would result in excessive wear between the control rod 5 and the eccentric shaft 6. Meanwhile, the driving moment of the eccentric shaft 6 is in positive correlation with Fc, Fc is increased, the driving moment of the eccentric shaft 6 is also increased, the volume and the mass of a driving device of the eccentric shaft 6 are increased, and the consumed energy is increased.
The distance from the connecting rod neck 42 to the connecting rod 2 is L6, and the distance from the connecting rod neck 42 to the control rod 5 is L7, that is, the distance from the connecting rod neck pin C to the line connecting the center of the piston pin a and the center of the connecting rod pin B is L6, and the distance from the connecting rod neck pin C to the line connecting the center of the control rod pin D and the center of the drive shaft 61 is L7.
Referring to fig. 2, an included angle between a central connecting line of the main journal 41 and the connecting journal 42 and a motion track of the piston 1 is CA, and when CA is larger than-40 degrees and smaller than or equal to 120 degrees, L6/L7 is 0.7-1, so that Fb is larger than Fc.
Specifically, when the angle CA is in the range of-40 ° to 120 °, the gas in the cylinder is compressed and burned, the pressure of the gas is high, and the cylinder explosion pressure F to which the piston 1 is subjected is large. The force Fa of the connecting rod 2 to the adjusting element 3 is larger, and the range of L6/L7 is ensured to be 0.7-1, so that Fb is ensured to be larger than Fc.
The above conditions make it possible to reduce the force Fc exerted by the adjustment element 3 on the control rod 5, reducing the wear of the control rod 5 and the eccentric shaft 6, the less energy it takes to drive the eccentric shaft 6. And simultaneously, the force Fb borne by the crankshaft 4 is larger, so that the power performance of the engine is not influenced. The adjusting element 3 transmits most of the force provided by the connecting rod 2 to the crankshaft 4, reducing the stress on the eccentric shaft 6.
Fb is positively correlated with L6/L7 and Fa, and Fc is positively correlated with L6/L7 and Fa.
Specifically, the relationship between Fb and Fa is Fb ≈ L (1+ L6/L7) × Fa, and the relationship between Fc and Fa is Fc ≈ L6/L7 ≈ Fa.
The size of L6 can be changed by changing the swing angle of the connecting rod 2, the size of L7 can be changed by changing the swing angle of the control rod 5, or the sizes of L6 and L7 can be changed by changing the relative rotation angle of the adjusting element 3 and the sleeved connecting rod neck 42 or changing the size of the adjusting element 3, so that the sizes of Fb and Fc are changed, and the stress condition of the compression ratio adjusting mechanism 7 is improved.
According to the engine of the embodiment of the invention, the stress condition of the compression ratio adjusting mechanism 7 is improved by adjusting the arrangement structure or the size of parts of the compression ratio adjusting mechanism 7, so that the force transmitted to the eccentric shaft 6 is smaller, the abrasion condition of the control rod 5 and the eccentric shaft 6 is reduced, the friction force between the control rod and the eccentric shaft is reduced, the driving force of the eccentric shaft 6 is reduced, and meanwhile, the force transmitted to the crankshaft 4 is large enough, and the power performance of the engine is not influenced.
Further, when CA is more than or equal to 30 degrees and less than or equal to 40 degrees, L6/L7 is 0.7-0.8.
Specifically, when the angle CA is in the range of 30 ° to 40 °, the cylinder interior gas is in the highest pressure state. The force F borne by the piston 1 is close to the maximum value, the force Fa of the connecting rod 2 to the adjusting element 3 is close to the maximum value, the range of L6/L7 is additionally controlled, and the range of L6/L7 is ensured to be 0.7-0.8.
The above conditions make it possible to obtain a sufficiently small force Fc of the adjustment element 3 on the control rod 5, minimizing the wear of the control rod 5 and the eccentric shaft 6, whereby less energy is consumed for driving the eccentric shaft 6. At the same time, the force Fb applied to the crankshaft 4 is large enough not to affect the dynamic performance of the engine.
The engine of the above embodiment may be applied to an automobile.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. An engine, comprising:
a piston (1), the piston (1) being movable within a cylinder (8) of the engine;
a crankshaft (4), a main journal (41) of the crankshaft (4) being rotatably provided on a cylinder block of the engine;
the adjusting element (3) is sleeved on a connecting rod neck (42) of the crankshaft (4);
a connecting rod (2), the connecting rod (2) being connected between the piston (1) and the adjusting element (3);
a compression ratio adjustment mechanism (7), the compression ratio adjustment mechanism (7) for adjusting the position of the piston (1) within the cylinder (8), the compression ratio adjustment mechanism (7) comprising: a drive shaft (61), an eccentric (62) and a control rod (5), the drive shaft (61) being rotatably disposed on the cylinder, the eccentric (62) being disposed on the drive shaft (61), a first end of the control rod (5) being articulated with the adjusting element (3), a second end of the control rod (5) being articulated with the drive shaft (61) via the eccentric (62), a distance between a central axis (61a) of the drive shaft (61) and a central axis (4a) of the main journal (41) being L5, a distance between a center (62a) of the eccentric (62) and a central axis (61a) of the drive shaft (61) being R2, a distance between a center of articulation of the first end of the control rod (5) and a center (62a) of the eccentric (62) being L4, L5, R2, L4 satisfying the relations: L5-R2 < L4 < L5+ R2.
2. An engine according to claim 1, characterized in that the distance between the centre (62a) of the eccentric (62) and the centre axis (4a) of the main journal (41) is L46, the difference between the distances L46 and L4 being L, L satisfying the relation: l is less than 5 mm.
3. An engine according to claim 1, characterized in that the distance between the centre (62a) of the eccentric (62) and the centre axis (4a) of the main journal (41) is L46, the difference between the distances L46 and L4 being L, L satisfying the relation: l is less than 1 mm.
4. An engine according to claim 2 or 3, characterized in that the engine has a minimum compression ratio when the compression ratio adjusting mechanism (7) adjusts the piston (1) to a first extreme position; when the compression ratio adjustment mechanism (7) adjusts the piston (1) to a second limit position, the engine has a maximum compression ratio.
5. An engine according to claim 4, characterized in that during the movement of the piston (1) from the first extreme position to the second extreme position, there is L-0.
6. An engine according to claim 4, characterized in that when the piston (1) is in the first extreme position, L-0.
7. An engine according to claim 4, characterized in that the length of L46 when the piston (1) is in the first extreme position is smaller than the length of L46 when the piston (1) is in the second extreme position.
8. The engine according to claim 1, characterized in that the compression ratio adjustment mechanism (7) further comprises: the driving device is connected with the driving shaft (61) and is used for driving the driving shaft (61) to rotate.
9. An engine according to claim 1, characterized in that the first end of the connecting rod (2) is hinged with the piston (1) by means of a piston pin (a) and the second end of the connecting rod (2) is hinged with the adjusting element (3) by means of a connecting rod pin (B).
10. An engine according to claim 9, characterized in that the first end of the control rod (5) is hinged with the adjusting element (3) by a control rod pin (D), which are arranged on both sides of the connecting rod neck (42).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811639121.5A CN110671196B (en) | 2018-12-29 | 2018-12-29 | Engine |
| PCT/CN2019/129013 WO2020135672A1 (en) | 2018-12-29 | 2019-12-27 | Engine and automobile having same |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811639121.5A CN110671196B (en) | 2018-12-29 | 2018-12-29 | Engine |
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| CN110671196B CN110671196B (en) | 2021-07-20 |
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| WO (1) | WO2020135672A1 (en) |
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| WO2020135671A1 (en) * | 2018-12-29 | 2020-07-02 | 长城汽车股份有限公司 | Engine and vehicle having same |
| WO2020135670A1 (en) * | 2018-12-29 | 2020-07-02 | 长城汽车股份有限公司 | Engine and vehicle having same |
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Also Published As
| Publication number | Publication date |
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| CN110671196B (en) | 2021-07-20 |
| WO2020135672A1 (en) | 2020-07-02 |
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